Oscillating die and punch press combination



Feb- 25, 1964 F. M. L1T`TE L ETAL 3,122,042

OSCILLATING DIE AND PUNCH PRESS COMBINATION Filed Jan. 13. 1961 5 sheets-sheet 1 Feb- 25, 1964 F. M. LITTELL ETAL 3,122,042

OSCILLLATING DIE AND PUNCH PRESS COMBINATION Filed Jan. 13, 1961 5 Sheets-Sheet 2 DIREC T/ON FEED 0F Mfr/4 L .S TRIP MA TE R/AL Feb. 25, 1964 F. M. LITTELL ETAL oscILLATING DIE AND PUNCH PREss COMBINATION 5 sheets-sheet s Filed Jan. 13. 1961 jizz/@gioni C5; Zai/fer mm n@ uw NN -@IIHU [Il .A NWN.

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bum www wu Feb. 25, 1964 F. M. L11-TELL ETAL 3,122,042

oscILLATING DIE AND PUNCH PRESS COMBINATION Filed Jan. 15, 1961 5 sheets-sheet 4 Feb. 25, 1964 F. M. LITTELL ETAL 3,122,042

v oscILLATING DIE AND PUNCH PRESS COMBINATION Filed Jan. 13. 1961 5 Sheets-Sheer?l 5 Il" zzz United States Patent O 3 Ia?, oscirLarn-ie rhan runen raras CIvI-NA'IIN rederick Pf. Litteii, Winnetka, auf Chester M. Wiig, C iicagc, iii., assignors to F. Ii. Iiiteii Machine Company,

Chicago, Iii., a corporation of Iilincis .I n. 13, lfei, Ser. No. 82,555 9 Ciainis. (Cl. 8a 2'} The invention relates to combination feeding and shearing mechanism and has reference in particular to the feeding of metal stock material from a coil and to the cutting of the stock material into blanks of various shapes including trapezoids, parallelograms, squares and triangles.

A basic object of the invention resides in the provision of novel and improved osciliating mechanism for a conventional type shear wherein said mechanism will be hydraulically actuated and with means being provided for adjusting the oscillating mechanism so as to vary the angle of cut.

A more specific object is to provide oscillating mechanism for a conventional type shear and which will be actuated as regards its cutting strokes in timed relation with the feeding means for the metal stock material and also in timed relation with any oscillating movement that may be imparted to the shearing structure.

Another object of the invention is to provide oscillating shear mechanism which will be driven from an oscillating power unit which in turn will be actuated by an hydraulic liuid.

A further object of the invention is to provide oscillating shear mechanism which will be actuated by a cam the eccentricity of which can be adjusted by the operator and wherein the operator can also vmy within limits the angular adjustment of the cutting knives with respect to the direction of feed of the metal stock material.

A further object resides in the provision of shearing mechanism as described which Will produce blanks of various trapezoidal and triangle shapes and which will incorporate improved journailing means for the retaining plates on which the cutting knives are mounted.

A further object is to provide oscillating mechanism of the character described wherein the retaining plates for the upper and lower knives are operatively connected so as to oscillate as a unit and which additionally permits reciprocating movement of the knives relative t each other to effect a cutting stroke.

A further object is to provide oscillating shear mechanism of improved construction and operation and wherein the holsters of the shearing structure have relative reciprocating movement for a cutting operation whereas the retaining plates for the cutting knives are so retained by the bolsters as to permit oscillating movement as a unit for producing cuts of diderent angles to the direction of feed.

With these and various other objects in view, the invention may consist of certain novel features of construction and operation, as will be more fully described and particularly pointed out in the specification, drawings and claims appended thereto.

In the drawings which illustrate an embodiment of the device and wherein like reference characters are used to designate like parts FIGURE l is an end elevational view of the metal feeding and shearing apparatus of the invention, the same showing a preferred form of intermittent feeding mechanism for driving the feed rolls for the metal stock material;

FIGURE 2 is a sectional View taken substantially on line 2 2 of FIGURE 3 but showing in plan elevation CAQ ldg

Patented Fei). 25, i964 ice the lower bolster plate and the eccentric drive mechanism for oscillating the shearing structure of the apparatus;

FIGURE 3 is a vertical sectional view taken substantially along line 3 3 of FIGURE 2;

FIGURE 4 is a vertical sectional view taken substantially along line 4 4 of FIGURE 2 and showing certain details of the hydraulically powered rack and pinion oscillating unit;

FIGURE 5 is a horizontal sectional View taken substantially along line 5 5 of FIGURE 4;

FIGURE 6 is a Ivertical sectional View taken substantially along line 6 6 of FIGURE 2;

FIGURE 7 is an enlarged sectional View showing the shearing knives and the indexing and clamped plates, the same being taken substantially along line 7 7 of FIGURE 3;

FIGURE S is a plan elevational view similar to FIG- URE 2 but illustrating a modification coming Within the invention;

FIGURE 9 is a vertical sectional View taken substantially along line 9 9 of FIGURE 8;

FIGURE l0 is a detail sectional View taken substantially along line lil-1t] of FIGURE 8; and

FIGURE 11 are views showing the various shapes that may be cut by the oscillating shear of the invention.

The apparatus selected for illustrating the invention is shown in FIGURE l as including a supporting frame structure l made up of a bottom wall 11 having leg elements I2, a front wall (not shown), a back wall `13 and side walls I5 and 16. A top wall 17 substantially completes the frame structure and said top Wall provides the support for the oscillating shear mechanism of the invention. The numerals 18 and 19 indicate auxiliary walls for supporting the feed rolls 2% and 22, of the feeding mechanism and which are suitably supported by the top wall 24 having connected relation with the auxiliary walls l and 19. The intermittent feeding mechanism shown in FIGURE l is able to feed measured lengths of metal stock material to an accuracy of several thousandths of an inch. Such accuracy is made possible by variating means which are provided for the oscillating arm 3? and by an arrangement of the various parts whereby a feeding stroke is produced for the major portion of the cycle with a non-feeding stroke or quick return taking place for a minor portion of the cycle. lIn this respect the feeding mechanism incorporates the improvements disclosed and claimed in the U.S. patent to Wiig 2,756,994, granted July 3l, 1956, and entitled Intermittent Feeding and Cutting Machine With Variating Means.

The drive shaft 2S imparts rotation to the crank which is iixed to said shaft and the said crank has a pin 27' which is operatively connected to the block 23. Said block 2S is adapted to reciprocate within the guide ways 29 provided therefor in the oscillating arm 35i, the said oscillating arm being pivotally mounted by means of the eccentric pivot 3i. The arm Sii also includes a rack portion 32, the outer free end of which is provided with a second block 33 also adapted to reciprocate within guide ways such as 34 and being adjustably positioned within said guide ways by the threaded adjusting screw 35. The reciprocating rack 36 is pivotally connected to block 33 by the pin 37 and thus said rack is reciprocated by the oscillating movement imparted to the arm 39.

The main drive 25 is rotated in a clockwise direction as shown in FIGURE l and thus as the shaft rotates from the position it assumes in said figure to a corresponding low position, it will have completed what has been described as a feeding stroke in approximately 230 degrees of rotation. The rack 36 will be drawn downwardly by the resulting movement of the oscillating arm Si) and due to the one-way clutch associated with the feed rolls 29 and 2.2, as will be presently described, the feed rolls are rotated during this feeding portion of the operating cycle. As shaft 25 continues to rotate in a clockwise direction, its effect will be to move the oscillatlng arm 3i) in an upward direction to its original elevated position of FIGURE 1. The rack 36 is given similar upwardrmovement which, however, does not rotate the feed rolls, since the clutch is merely caused to overrun. This non-feeding cycle is accomplished in approximately 130 degrees of rotation. As a result of this relatively slow feeding action with quick return during the non-feeding stroke, a more accurate feed stroke is obtained. It is also possible to vary the length of the feed stroke d uring operation by adjusting the eccentric pivot 31 which provides the variating means previously referred to. Of course, the basic stroke length is obtained for each particular job by adjusting the block 33, by rotation of the threaded screw 35.

The lower feed roll Ztl and the upper feed roll 22 Yare suitably journalled for rotation with the upper roll Ybetween the pinion 41 and the feed roll 2G and said clutch is so constructed and arranged that only reciprocating movement of the rack in a downward direction is imparted to the feed roll 2@ and thus to the feed roll 22 to produce a feeding action of the rolls. Accordingly metal stock material having location between and being gripped by the rolls will be fed to the knives of the oscillating shear mechanism. The action of the one-way clutch is fully explained in the US. patent previously referred to.

The top wall 17 comprising the bed plate of the press as shown in FIGURE 3, provides the support for the lower bolster 42 which is suitably iixed to said bed plate by means not shown. The bed plate 17 also supports the tubular guide posts 43 which extend vertically upward from the same and which are telescoped by the coacting and depending posts 44. The said posts 44 depend from the top support member 45 which may be described as the ram of the press. The said posts accordingly support the top member 4S in'a manner which permits vertical reciprocating movements thereof toward and from the lower support, that is, the bed plate 17. The tubular and coacting posts 43 and 44 are respectively located at the four corners of the shear structure and the said posts enclose actuating means for reciprocating the top support 45 whereby to effect a cutting operation of the cutting knives of the oscillating shear. The actuating means for reciprocating the cutting knives is conventional Vin structure and operation and the same are not shown. The upper bolster 46 is xedly secured to the top support 45 by means of the screws 47. Accordingly it will be understood that the lower bolster'42 does not move in any manner at all. However, the top support member 45 and the top bolster 46 form a unit and have vertical reciprocating movement as described.

The top bolster 45 has peripheral anges 5h extending around its base on diametrical sides and the peripheral lianges are engaged by the retaining members 51 which are secured to the retaining plate 52 by the screws 53. The top bolster 46 accordingly retains the retaining plate 52 in a manner which permits oscillating movement of the retaining plate with respect to the bolster. For the purpose, the journalling stud 54 is provided and which is suitably mounted for free rotation in bolster 46 by means of the ball bearing race S. The said journal stud depends a short distance below the bolster so as to enter and center the retaining plate 52 for rotation. The said plate 52 has the upper knife 56 secured thereto so as to depend from the retaining plate as best shown in FIGURE 7. This ligure clearly shows the journalling stud 54 as depending into the retaining plate 52, and also illustrates how the screw 57 securely locks the journalling stud to the said retaining plate.

The longitudinal member 5S is secured as by welding to the retaining plate 52 and said member is backed by the angle pieces 5). The upper blade 56 is secured to the longitudinal member 58 by the screws 61 and thus the knife S6 is releasably but ixedly secured to said retaining plate 52. The pressure foot 62 is disposed adjacent knife 56 and the pressure foot is resiliently biased by the coil spring 63 so as to retain the metal stock material such as 64 in pressure contact with the rear table support plate 65.

The top retaining plate 52 is operatively associated with the lower retaining plate 66, FIGURE 3, by means of guide pins 67 and 68 located at respective ends of the retaining plates. T le said guide pins are fixed to the upper retaining plate 52 by having a press t in the plate and thus the guide pins depend from the plate at each end, respectively. The said guide pins enter and are telescoped by the bushings 7S which are retained by the lower retaining plate 66, the bushings being held to the plate 66 by having reduced lower ends which fit into openings 71 in the plate. The guide pins tie the top cutting structure to the lower cutting structure so that the combined unit will oscillate as a unit while permitting the upper retaining plate 52 and the top knife 55 to reciprocate with respect to the lower knife 72, all as will be clearly understood from FIGURES 3 and 7.

Lower knife 72 is releasably secured to the longitudinal member 73 by means of the screws 74. The said member 73 is secured as by Welding to the lower retaining plate 66 and the said member 73 is rigidly backed by the angle members 75. An apron 77 is fixed by the screws 78 to the retaining plate 66 and the front table support Si? is likewise fixed by the screw Si to said retaining plate. The table support Si) is additionally anchored and positioned by means of a pin 82.

The clamp plate indicated by numeral 83 in FIGURE 2 has a characteristic shape, the same having flat sides 84 and arcuate ends SS. Said clamp plate lits within a recess provided thereby in the undersurface of the retaining plate 65 as shown in FIGURE 3, and the position of the clamp plate 83 therefore determines the position of the cutting knives 56 and 72 and the associated shear structure with respect to the direction of feed. The clamp plate is adjusted by means of an indexing plate 86 which also tits within a recess provided therefor in the top surface of the bolster 42. The indexing plate 86 also functions as a part of the drive for the oscillating 'shear and the same is, therefore, journalled along with the clamp plate by means of a journalling stud 87 rotatably mounted by the ball bearing races 8S in `the bolster 42. The stud 87 provides a part 90 which interfits between Ythe clamp plaie s3 and the indexing plate ss, FIGURES 3 and 7, and the part 99 thus centers the two plates for rotation on the same vertical axis. From part 9b a stem 91 projects upwardly and the stem is centered in an opening in the lower retaining plate e6. The clamp plate 83 and the indexing plate 85 are thus rotatable on the same axis and with respect to the bolster 42.

The adjustment of the clamp plate 83 requires that the operator release the clamp locks 92 and 93, each lock having its own locking and releasing screws such as 94 for the clamp lock 92 and `95 for the clamp lock 93. When the screws are released the clamp plate 83 is free to be rotatably adjusted or indexed, and this requires a special tool of the chuck type and which is inserted in the opening 96 provided for the same in the clamp lock 93. Said opening 96 has centering relation with opening 97 in the indexing plate 86 so that the end of the tool enters opening 97 with its teeth being located in opening 96. The teeth of said tool will, therefore, engage teeth 9S provided by the clamp plate 83, and thus rotation of the tool will rotate the clamp plate with respect to the indexing plate. In order that the operator may visually note the extent of indexing movement or adjustment given to the clamp plate, it is preferred that indicia be located on clamp plate 33` with a pointer having location on plate 36.

FiGURE 7 illustrates the manner of locking the plates following an indexing operation. lt will be observed that plate o3 has a sloping peripheral edge indicated by numeral iti@ and these are in turn engaged by the slop .g complementary walls lill provided by the respective clamp loclrs 92 and 93. When the screws $4 and 9S are tightened, the clamp plate 53 is securely bolted and secured to the indexing plate Se. ri`he lower bolster i2 is provided with the peripheral iianges ld?.y on diametrical sides and the flanges are engaged by the retaining members ftd?) which are secured by screws to the lower retaining plate 6o.

lt has been previously stated that the indexing plate Se is part of the oscillating drive for the shear mech sin and thus said shear mechanism is caused to oscillate on the vertical as provided by the stud 87. For this purpose the bolster 42 is recessed to yform the arcuate cavity FiGURES 2 and 8. Said cavity is in cornmunication with and forms part of the passageway l e, also formed in the boister z2 as clearly evident trom FlG' RE 6. The passageway accommodates a connecting rod indicated by numeral ldd which at its outer end has operative connection wtih an eccentric operating cam il@ and at its inner end the connecting rod has connection with the indexing plate by means of the drive pin Stil. Said pin is iournalled in the inner end of the connecting rod ldd by the ball bearings liZ and the pin nas an enlarged intermediate portion which is recessed into the plate so as to interconnect with the indexing plate. The stem ll ot the drive pin is received in an opening in the indexing plate so that pin lil operatively connects the rod iti-S with the said indexing plate Se whereby to transmit to the plate the reciprocating movements of th said connecting rod.

The connecting rod at its outer end terminates in a ring lid which encircles the operating cam lll@ and i ictional engagement with the periphery of said cam. This operative connection oi the connecting rod with the earn provides for rotation oi the cam and reciproca-.tion oi the rod to a degree which is dependent on the eccentricny o the operating cam. The operating cam is rotated rst in one direction and then in an opposite direction by an hydraulic power unit indicated in its entirety by the numeral lid, FIGURE 5. The bolster 42. has

tion .egral therewtih which provides an encio f ng the power unit le which i cludes spaced side walls 'lle and il? a the bottom wall ld. The power unit is located wrt: n and s ably secured to the rear wall if by means oi the securing bolts lll and the unit is supplied with an duid un der pressure by means ot the pipes and ZS which pass through openings in the end wall ll'.

The power unit essentially consists of a walled container, the same including tour longitudinal walls such as the bottom and top walls i253- and 12S and the two side walls E and i217, and with the resulting structure being enclosed by end wadls i253 and Within the walled enclosure the unit provides two reciprocating racks 125i md 132, and ywhich have meshing relation wtih the pinion fixed to and providing part of the operating shaft By means of various passageways formed in the walls of the unit and which commu icate with the hydraulic t upply pipes E22 and lZS, the racks il and i322 are given simultaneous movement in opposite directions. As shown in r- (EURE 5 rack it operating above center partition has been caused to travel to the right, whereas raclr 3.32 operating below the center partition i135 -las been caused to travel to the lett, all as a result of hydra ilic fluid under pressure being supplied to pipe "H3, This movement o the racks will impart clockwise rotation, EIC-URE 5, to the pinion i325 and thus to the operating shaft 134. However, upon the pressure duid being supplied to pipe 122-, the racks ll and 32 will be caused to travel to the left and to the right, respectively. 7When the raclrs move in this direction, the pinion 133 and the shaft i3d are rotated countercloclrwise. As best shown in FTC-URE 4 the depending end of the operating shaft i3d is provided with an arm i3d which is adapted to alternately Contact the limit switches i3? disposed on opposite sides or" the shaft Etf-l. The limit switches control the liow of the hydraui'c fluid in the pipes l2?. and lid.

During operation of the hydraulic power unit the same accordingly produces rotation of the operating shaft i3d iirst in one direction and then in an opposite direction. his oscillating movement of the operating shaft as above described is imparted to the operating cam and structure is provided which permits adjustment of the eccentricity of the cam with respect to shaft i3d from Zero to a predetermined maximum such as may be necessary for cutting the stock material into lthe various Itrapezoidal and triangular shapes as shown in FiGUiaE ll. 'lhe upper projecting end or the operating shaft is formed at 13S with pinion teeth which ha e meshing relation with the slide members litl. The members are retained by' the operating cam 1i@ and in a manner which permits slidable movement of the opera lng cam with respect to the end i3d of the operating shaft. The hub member ld is associated with earn and with the guide members lt so as to have slidable movement along with the guide members relative to the cam litt. The hub member :141 accommodates the projecting end 'i412 oi the operating shaft and accordingly it will be understood that the hub member retains a fixed relationship with the operating shaft. However, the operating cam 11S' is adjusted with respect to the hub member 141 so as to vary the eccenticity of the operating cam and this is .ccornplished by the threaded adjusting screw 143 which has threaded relation with the hub member 141 `and is rotatably xed to the cam il@ by means of the member ill-d. Since this end of the adjusting screw lll-3v is rotata 1ly held by the cam lle, it will be seen that rotation of the screw 43 will etect adjustment of the cam whereby its eccentricity with respect to shaft 134 can be varied.

The hub member ll as shown in FGURE 2 is adjusted for zero eccentricity. Accordingly no oscillating movement will be imparted to the shear structure. In the event it is desired to out a blank such as i435, FiG- URE ll, no adjustment is required of the clamp plate S3, but it is necessary to change the adjustment of the cam llt? with respect to hub member ldl so that approximately 39 degrees eccentricity is obtained, that is, thirty degrees on respective sides of a median position A B as sh 'ai in RE 2. When the operating cam rotates in one direction, the indexing plate do having connection with the cam through the rod i538 and the pin lli, will be rotated in a clockwise direction, FiGUrl-E 2, so that the cutting shear at the end ot' the movement will assume a position substantially as indicated by dotted lines C-D. Upon the shear mechanism eecting a cutting stroke, the edge lo or" the blank lil-5 will be cut. rl`he opera ing carn litt now reveses its rotation and the indexing plate is rotated in a counter-clockwise direction, FEGURE 2, until the shear mechanism assumes the position indicated by dotted lines E-F. This latter position is approximately 60 degrees angularly displaced from position C-D and upon completion of the next cutting stroke of the shear mechanism, the edge 2147 of the blank 145 will be cut. in the operation of the parts as above described, the shear mechanism will oscillate approximately 30 degrees on opposite sides of a median position indicated by dotted lines A--B. The angularity of the side edges 146 and 147' of the blank can be varied within limits by varying the eccentricity of cam litt.

For cutting a trapezoid such as the blank 143 having sides which dider in angularity, it is necessary to adjust the relation of the clamp plate 83 with respect to the indexing plate 86. In other words the median position of the shear mechanism is changed so that the median position is not at right angles to the feeding direction. Accordingly when the operating cam lll) rotates in one direction, the cutting stroke of the shear mechanism produces the edge 159 on blank 148 and when the cam 110 rotates in an opposite direction, the next cutting stroke produces the edge lS-l.

lt is also possible to produce a parallelogram shape such as the blank 152 or a simple triangular shape such as the blank 153. For the parallelogram blank the eccentricity of the cam 119 is `adjusted to zero and the clamp plate 83 is indexed for the particular angle desired for the sides 154. Por the triangular blank the cam is again adjusted for the required eccentricity and Ithe plate is indexed at zero.

in the modification of the invention shown in FIG- URES 8, 9 and l0, the power unit for oscillating the indexing plate, -and thus the shear mechanism, is mounted for bodily movement in order to provide for adjustment purposes. With the power unit being capable of adjustment bodily so as to vary the median position of the shearing mechanism, it will be understood that the clamp plate and indexing means therefor can be omitted. Accordingly, in this modication the clamp locks 92 and 93 are not employed and the clamp plate 'S3 is an integral part of the indexing plate 86 and its retaining plate 66.

Referring again to said figures it will be observed that the indexing plate 3.86 is rotatably mounted on the lower bolster 142 by means of the pivot stud 167, and the same being rotatably mounted in the bolster 142 by means of ball bearing races and having a projected stem portion .191 which is received in an opening formed in the indexing plate. Also in this modification the bolster- '142 is provided with an arcuate recess 2% which is substantially a continuation of a passageway which accommodates the connecting rod 2%. The inner end of the rod journals the member 211 in the form of a pivot stud and which likewise has la top projecting stem portion 213 which in turn operatively connects with the plate 186 since the stem 213 is received in an opening formed in the plate. Accordingly any reciprocating motion irnparted to the connecting rod 26S will be transmitted to the plate 186 and thus oscillating movement of the plate is provided `for and the same is permitted by reason of the arcuate recess 205 for-med in the bolster 142. Of course, it Will be understood that the loiV er retaining plate 66 has suitable securement to plate 186 and thus the enf tire supporting structure for the upper and lower cutting knives is initially located in a median position by the particular positioning of plate 185. Oscillating movement of the plate `and thus the cutting knives will take place on respective sides of the median position, depending on the magnitude of the reciprocating strokes of the connecting rod 208 and which in turn depends on the eccentricity of the eccentric cam 21%.

In this modication the eccentric cam 2l@ is operatively connected with the operating shaft 234, all as previously explained, and the outer projecting end of the connecting rod 2% is provided with the rhig portion 214 which has encircling relation with and frictional contact with the periphery of the eccentric cam 2li?. Also as previously described the hub mem er 241 is operatively associated with the operating shaft 234 by means of the stem portion 242 and the hub member and eccentric cam are relatively adjustable all in a manner as previously described in order to vary the eccentricity of the cam 2l@ and thus the magnitude of the reciprocating strokes of the connecting rod 29S.

The frame structure which is formed integrally with the lower bolster 142 includes the side walls 2lb and Zl and the end wall 2219, the latter being releasably fixed to the side walls by the securing screws 22o-l. The hydraulic power unit indicated in its entirety by numeral Zl is located within the supporting structure, being slidably mounted within the groove provided by the side walls 216 and 217 by means of the laterally extending elements 224 and 225 which for this modication constitute part of the power unit. The pipes 222 and 223 comprise the supply pipe for the high pressure fluid which is alternately delivered by said pipes to the power unit. For controlling flow of said high pressure fluid the operating shaft 234 is provided with the member 236 which alternately contacts with the limit switches 237 located on respective sides of the operating shaft, it being understood that the said shaft will have rotation first in one direction and then in an opposite direction as a result of the reciprocating movements given to the rack'members located within and forming the operating elements' of the hydraulic power unit.

Adjustment of the power unit 215 within the frame structure supporting the same is effected by the gear wheels 24@ and 24l, the same having threaded relation with the threaded studs 242 and 243, respectively. The threaded studs are fixed to the rear wall of the power unit 215 so as to project therefrom and as best shown in FEGURE 8 it will be observed that the studs extend through openings in the spaced walls 244 and 245 integral with and provided by the rear wall 2l9. The gear wheels 24h and 241 have location between the spaced walls and it is possible to rotate the said gear wheels simultaneously by rotating the pinion 246 which has meshing relation therewith. The pinion is journalled by a stud which terminates in a squared end 247 so that when the locks 24S are released it is possible to rotate the gear Wheels 244i and 241 by applying a tool to the squared end 247, and rotating pinion 246. Since the gear wheels are held between the spaced walls, their action will be to either withdraw or propel the threaded studs 242 and 243, and accordingly bodily movement for adjusting the median position of the shear structure will be given to the power unit 215.

The invention is not to be limited to or by details of construction of the particular embodiment thereof illustrated by the drawings, as various other forms of the device will, of course, be apparent to those skilled in the art without departing from the spirit of the invention or the scope of the claims.

What is claimed is:

l. In oscillating shear mechanism of the character described, the combination including a lower knife and an upper knife adapted to coact therewith, a supporting structure for said knives, said structure including a retaining plate having the lower knife fixed thereto and a second retaining plate having the upper knife fixed thereto, guide posts fixed to one retaining plate and having slidable connection with the other retaining plate, whereby the said plates and thus the knives may be reciprocated for effecting a cutting operation, means mounting the supporting structure for oscillating movement independently of said reciprocating movement, the axis of said oscillating movement being located approximately centrally of the supporting structure, an hydraulic unit providing an operating shaft, said shaft rotating first in one direction and then in an opposite direction when operative, and an eccentric cam associated with the operating shaft and eing oscillated thereby for in turn oscillating the supporting structure.

2. Gscillating shear mechanism as defined by claim l, additionally including adjustable means associated with the operating shaft and with the eccentric cam for varying the eccentricity of the cam with respect to the shaft.

3. In apparatus for cutting metal blanks of Various shapes from strip material intermittently fed thereto, the combination including a lower knife and an upper knife adapted toY coact therewith, a supporting structure for said knives including a retaining plate having the lower knife fixed thereto and a second retaining plate having the upper knife fixed thereto, guide posts fixed to one retaining plate and having slidable connection with the other retaining plate, whereby the said plates and thus the nives may be reciprocated for eifecting a cutting operation, means mounting the supporting structure for oscillating movement independently of said reciprocating movement, the axis of said oscillating movement being located pproximately centrally of the supporting structure, a power unit for oscillating the said supporting structure, an eccentric cam driven by said power unit, a connecting rod having connection at one end with the eccentric cam, and adjustable means pivotally joining the connecting rod at its other end with one of said retaining plates.

4. Apparatus for cutting metal blanks of various shapes from strip material as delined by claim 3, additionally including other adjustable means associated with the eccentric cam for varying its cccentricity, and wherein the connecting rod is pivotally joined to the retaining plate having the lower kniie fixed thereto.

5. Apparatus for cutting metal blanks of various shapes from stri material as defined by claim 3, wherein the power unit includes an operating shaft adapted to be dratnicaily rotated first in one direction and then in an joined to retaining plate having the lower knife iixed thereto, and additionally including other adjustable means associated with the eccentric cam and with the operating shaft for v ing the eccentricity of the cam with respect to the operating shaft.

6. ln apparatus for cutting metal blanks of various shapes from strip material intermittently fed thereto, the combination including a lower bolster, an upper bolster positioned in spaced relation above the same and supported for reciprocating movements toward and from the lower bolster, a lower knife and an upper knife adapted to coact therewith, a supporting structure for said knives including a retaining plate having the lower knife xed thereto and a second retaining plate having the upper knife xed thereto, guide posts xed to one retaining plate and having slidable connection with the other retaining plate, whereby the said plates and thus the knives may be reciprocated for eecting a cuttinU operation, said supporting structure having location between the upper and lower bolsters and with the upper and lower retaining plates having contact with the upper and lower holsters respectively, a pivot stud mounted in each bolster on the same vertical `axis and extending into the retaining plate in contact with its bolster, whereby the supporting structure is mounted for oscillating movement independently of the reciprocating movements of the upper bolster, the second retaining plate and knife, an hydraulic unit providing an operating shaft, said shaft rotating first in one direction and then in an opposite direction when operative, andan eccentric cam associated with the operating shaft and being oscillated thereby for in turn oscillating the supporting structure.

7. In apparatus for cutting metal blanks of various shapes from strip material intermittently fed thereto, the combination including a lower stationary bolster, a lower retaining plate supported on the lower bolster for oscillating movement about a vertical axis approximately centrally of the length of the plate, a lower cutting knife fixed to the lower retaining plate, an upper bolster supported above and in spaced relation with the lower bolster and in a manner permitting reciprocating movement of the upper bolster toward and from the lower bolster, an upper retaining plate suspended from the upper bolster and adapted to oscillate with respect thereto ou the said vertical axis, an upper cutting knife fixed to the upper retaining plate, guide posts fixed to one retaining plate and having slidable connection with the other retaining plate, whereby said retaining plates and knives can be oscillated as a unit and independently of the reciprocating movement of the upper bolster, upper retaining plate a-nd knife, an indexing plate retained by the lower bolsterand adapted to have oscillating movement with respect to the lower bolster, a clamp plate in contact with and supported by the indexing plate in an adjusted rotated position with respect to the indexing plate, a connecting rod, means operatively connecting the rod to the said indexing plate, an eccentric cam for imparting reciprocating movements to the connecting rod, and means for varying the eccentricity of the said cam, said clamp plate and indexing plate comprising an operative part of the lower retaining plate.

8. Apparatus for cutting metal blanks of various shapes from strip material intermittently fed thereto as defined by claim 7, additionally including clamp locks for releasably locking the clamp plate to the indexing plate in an adjusted rotated position with respect to the indexing plate, wherein a power unit is provided, the same having an operating shaft which is rotated first in one direction and then in an opposite direction when the power unit is operative, and wherein the eccentric cam is iixed to and oscillated by the said operating shaft.

9. Apparatus for cutting metal blanks of various shapes from strip material intermittently fed thereto, the combination including a lower knife and an upper yknife adapted to coact therewith for eifecting a cutting operation, a supporting structure supporting said upper knife in a manner permitting reciprocating movements thereof toward and .from the lower knife, means mounting the supporting structure for oscillating movement independently of said reciprocating movement, the axis of said oscillating movement being located approximately centrally of the supporting structure, and power means for oscillating the supporting structure including an hydraulic unit providing an operating shaft adapted to rotate tirst in one direction and then in a reverse direction when the unit is operative, an eccentric cam actuated by the operating shaft, means operatively connecting the eccentric cam with the said supporting structure, and means mounting the hydraulic unit for bodily adjusting movement whereby to vary the median position of the supporting structure.

References Cited in the le of this patent UNITED STATES PATENTS 524,501 Kendall Aug. 14, 1894 2,197,043 Guyler Apr. 16, 1940 2,751,260 laniszewski June 19, 1956 2,767,789 Budlong Oct. 23, 1956 2,823,960 Blazek Feb. 18, 1958 2,920,521 Abbenante Jan. 12, 1960 

1. IN OSCILLATING SHEAR MECHANISM OF THE CHARACTER DESCRIBED, THE COMBINATION INCLUDING A LOWER KNIFE AND AN UPPER KNIFE ADAPTED TO COACT THEREWITH, A SUPPORTING STRUCTURE FOR SAID KNIVES, SAID STRUCTURE INCLUDING A RETAINING PLATE HAVING THE LOWER KNIFE FIXED THERETO AND A SECOND RETAINING PLATE HAVING THE UPPER KNIFE FIXED THERETO, GUIDE POSTS FIXED TO ONE RETAINING PLATE AND HAVING SLIDABLE CONNECTION WITH THE OTHER RETAINING PLATE, WHEREBY THE SAID PLATES AND THUS THE KNIVES MAY BE RECIPROCATED FOR EFFECTING A CUTTING OPERATION, MEANS MOUNTING THE SUPPORTING STRUCTURE FOR OSCILLATING MOVEMENT INDEPENDENTLY OF SAID RECIPROCATING MOVEMENT, THE AXIS OF SAID OSCILLATING MOVEMENT BEING LOCATED APPROXIMATELY CENTRALLY OF THE SUPPORTING STRUCTURE, AN HYDRAULIC UNIT PROVIDING AN OPERATING SHAFT, SAID SHAFT ROTATING FIRST IN ONE DIRECTION AND THEN IN AN OPPOSITE DIRECTION WHEN OPERATIVE, AND AN ECCENTRIC CAM ASSOCIATED WITH THE OPERATING SHAFT AND BEING OSCILLATED THEREBY FOR IN TURN OSCILLATING THE SUPPORTING STRUCTURE. 